Fluid pressure regulator



March 9, 1954 l.. E. BALDWIN FLUID PRESSURE REGULATOR 2 Sheets-Sheet Filed Sept. 15, 1948 w :ills

5 t". /.ow/N,

INVENTOR.

March 9, 1954 E. BALDWIN 2,671,463

FLUID PRESSURE REGULATOR FiledSept. l5, 1948 2 Sheets-Sheet 2 5mm/w EE NVENTOR.

Patented Mar. 9, 1954 FLUID PRESSURE REGULATOR Lee'E. Baldwln,.Glendale, Calif., assignor to Weston Hydraulics, Limited, North Hollywood, Calif., a corporation of California Application September 13, 1948, Serial No.49,111

11 Claims.

invention relates generally toy fluid pressure regulators, and more' particularly,` toa pressure reducing valve for use in uid'pressure actuated remote control systems.

In servo systems involving fluid pressure operated devices, such for example, as the control systems in aircraft, it is frequently the` practice to provide a supply reservoir of the actuating uide.`g., air or liquid, which is, maintained at a pressure considerably higher than the operating pressure. Such high pressure storage reservoir is maintained'at a pressure which may vary somewhat but isnormally always greater than the operating* pressure. It is accordingly Ynecessary to provide a regulator orpressure`reducer inthe' linefrom the reservoir to the cperating control.

Several features aredesirable in a pressure reducer for the purpose just'stated'which have not always been 4found in devicesheretofore available. Among such desirable features are the y following.

First, the pressure reducer should includeV a valve element which operates extremely rapidly to restore pressure whenever the working. pressure drops below a predetermined value. It is also desirable-that when the valve operates to admit fluid from the reservoir into the working system that it close quickly when` the working pressure has been restored tothe desired value,

and that oscillatory surgesfaboveand below the working pressure be avoided. In previous devices wherein the movable valve element, combined with the pressure sensitive element required to open and close it, is relatively large and massive, the tendency is for the valve to resist: openingA and rclosing due to the inherent inertia.v of the movable element, and due also to 'the static friction which must be-overcome 'to initially move large members. The result vof this is that the working pressure must drop a considerable amount below the normal level 'bevforethe valve opens appreciably. Furthermore, when the working pressure is restored to normal, .the valve does not close immediately, allowing a surge above vthe normal working pressure and' if relief' valves or other'means are prou kvided'toA relieve the pressure in the working system, the pressure is again dropped a little-below normal, thus producing an oscillatory pressure surge above and 'below the `normal working level.

'This is an undesirable condition, particularly in aircraft controls where such oscillations may reilect themselves in mechanical'movementiof control surfaces or other hydraulic orA air-actuated Another desirable feature to be incorporated in high pressure storage systems of the class described involvesareturn of the actuating fluid from the workingtsystem to` the reservoir in the event of temporary or permanent loss of reservoir pressure. Such is a particularly valuable feature in air-actuated systems. For example, should the high pressurereservoir ,be damaged so as to release the uid stored therein, vthere still may be suflicientuid under pressurein some of the actuating cylinderszofi'the working system to actuate others off said cylinders. Thus, if a check valve is employedaatthe exit of the reservoir so as to entrap Aally pressurizedfluid throughoutthe system (bothhigh `pressure and working), it then is possible by providinga reverse flow check'valve' inv the'pressure reducer to permit fluid from someparts oftheworkingy system to return to the high pressure system for distribution to other parts of the working system.

Still another desirable feature in systems of the class described is a relief valve' to permit y'release of excess'fluid from the working system should the pressure therein, for any reason, exceed the normal working pressure. Such increase kmay occur, for example, by reasoncf thermal expansion, or may occur for other reasons.

Bearing in mind the foregoing desirable characteristics, it is a major object of the present invention to provide a pressure 'reducing valve'of the class described having a valving element of extremely low inertia whereby to avoid oscillatory pressure surges as `above described.

It is another Aobject kof the invention `to provide in a valve of the class described, a return check valve by which fluid in the working system may bek returned to the high pressure storage system in the event of depletion of the storage reservoir.

rStill another object of the invention is to provide in a valve of the class described, a simplied relief valve for relieving excess pressure in the working system.

Afurther object of the invention is to provide a valve of the class described in which the forces acting on the'movable valve element by reason of vfluid'pressures are substantially balanced out.

A still further object ofthe invention is to provide a pressure reducing valve as described 'which is adapted'for quantity'production' and is easily disassembled and reassembled for purposes of maintenance and repair. r

The foregoing and otherobjects and advantages of the invention will become apparentfrom va lconsideration 'of the following detailedY deu. scription, such consideration being given also to the attached drawings, in which:

Figure l is a semi-schematic diagram illustrating the connection of a valve embodying the present invention in an air-actuated control system;

Figures 2 and 3 are axial sections taken through a simplified version of a valve embodying certain features of the present invention and serve as operational diagrams;

Figure 4 is an end elevational view of a presently preferred form of pressure reducing valve embodying the present invention;

Figure is an elevational section taken on the line 5-5 in Figure 4; and

Figure 6 is an elevational partial section taken on the line 6 6 in Figure 5.

In the diagram in Figure 1, the pressure reducing valve embodying the present invention is designated by the reference character I0, and is connected in the system to reduce the relatively high pressure in a storage reservoir I I to a working pressure delivered through a conduit I2 to the working system. Fluid under relatively high pressure is delivered by a conduit |3 from the storage reservoir |I to the reducer valve ||l. A check valve I4 is provided at the exit of the reservoir I I to prevent counter-flow of the fluid from the conduit I3 into the reservoir II in the event that the reservoir should be damaged to re lease the fluid and pressure therein. A branch conduit I5 is provided which may lead to a second pressure reducing valve I0 supplying iluid to another portion of the working system.

Fluid delivered by the working pressure conduit I2 is controlled by a four-way control valve I 6 of conventional design which is adapted to deliver fluid at working pressure selectively through a conduit I'I to one end of a uid motor or actuating cylinder I8, through another conduit I9 to the other end of the cylinder I3, or

through a conduit to a pump 2| for compression and return to the storage reservoir II through a conduit 22.

A piston 23 is moved to the left or right (in Figure 1) depending upon which end of the cylinder I8 receives fluid under the control of the valve I6. Such fluid as is exhausted from the cylinder I8 by reason of movement of the piston 23 is returned through one of the conduits |'I or I9 to the control valve IB which is adapted to connect one or the other of said conduits I'I and I9 to the return conduit 20.

As previously stated, the storage pressure of the fluid in the reservoir I I may vary over a considerable range but is always greater than the normal working pressure required for the actuation of the piston 23 in the cylinder I8. Thus, the primary requirement of the valve I il is that it reduce this indeterminate storage pressure to a fixed and predetermined working pressure.

The basic elements required for this pressure reducing operation are illustrated in the semidiagrammatic views, Figures 2 and 3. The simplified valve Illa. illustrated in Figures 2 and 3 comprises a cylindrical housing 25 enclosed at the left end and provided with fluid connections I2 and I3. In Figures 2 and 3, the working pressure and high pressure connections I2 and I3 are indicated corresponding to the conduits I2 and I3 in Figure 1. From the high pressure conduit I3, fluid under storage pressure enters a chamber from which it may (under certain conditions) flow through a valve port 3| into a working pressure chamber 32, whence it is discharged into the working pressure conduit I2.

A valve member 33 slidably positioned on a valve stem 34 is positioned and adapted to cooperate with the valve port 3| to close the same when the working pressure in the chamber 32 reaches the predetermined normal value. A shoulder is formed in the valve stem 34 and positioned to engage the valve member 33 upon movement of the valve stem 34 to the right and open the valve member 33 as indicated in Figure 2. 1

Upon movement of the valve stem 34 to the left, the shoulder 35 is pulled away from its engagement with the valve stem 34 permitting a compression spring 35 to close the valve member 33 against the valve port or seat 3|. A pin 31 xed in the valve stem 34 is adapted to engage the valve member 33 to prevent motion of the valve stem 34 substantially greater than that required to close the member 33 against the seat 3|.

It should be noted that the valve stem 34 is extended outwardly to the right through the end wall of the housing 25, a fluid seal being provided to prevent escape of uid from the high pressure chamber 30.

The diameter of that portion of the valve stem 34 which extends to the right and out of the housing 25 is made substantially equal to the diameter of the valve port 3| whereby the force exerted on the valve member 33 due to the fluid pressure in the chamber 3|] is substantially balanced out in that the valve stem 34 has a force acting thereon tending to expel the stem through the right-hand end of the housing 25 which is approximately equal to the force exerted on the member 33 due to the attempted escape of fluid through the port 3|. In practice, it has been found desirable to make the diameter of the extending valve stem 34 slightly less (at its righthand end) than the diameter of the port 3|, thereby leaving a slight residual force operating in a direction to close the valve member 33.

In order to move the valve stem 34 to the right to open the valve member 33 when the working pressure in the chamber 32 drops below a desired minimum value, a movable piston 42 is slidably mounted in the housing 25 forming the left-hand closure of the Working pressure chamber 32. The piston 42 is urged to the right by a calibrated compression spring 43, the rate of the spring 43 being such that when the pressure in the chamber 32 is at the minimum predetermined value, the shoulder 35 is just engaging the valve member 33 in preparation to pushing the same to the right to open the port 3|. Motion of the piston 42 is transmitted to the valve stem 34 by engagement of the piston with a flange or shoulder 4I for'ned near the left end of the valve stem 34.

The valve stem 34 is slidable in the Piston 42, a fluid seal 44 being provided to prevent escape of fluid around the stem. The diameter of that portion of the valve stem 34 which extends through the piston 42 is also made substantially equal to the diameter of the port 3| whereby the forces exerted on the valve stem 34 by reason of the working pressure in the chamber 32 are substantially balanced out. In actual practice, the diameter of the valve stem 34 within the piston 42 is made slightly greater than that of the port 3| whereby to again leave a Slight residual force tending to hold the valve member 33 in its closed position.

A breather orifice 45 is formed in the left end of the housing 25 in order to permit air to leave or enterthe space behind the piston 42 during the movement thereof.

In operation of the valve Ia, high pressure fluid is introduced through the conduit I3 and since initially themev islno pressure'lin fthe chami berv32 to lcounteraotfthe force of the -rcalibrated spring J3, theval-ve. stem'34 isin its "rightfha'nd position holding thelvalve member .33 open and permitting fiuid to new throughthe valve Ia, and'outthroughthe .conduit I2. As the pressure in the'working system builds up, increasing force is :exerted against the right-hand 'face of the 'piston :112. When the force exerted against the piston 42 :bythe Vfluid pressure in the chamber 32 exceeds the pressure exerted bythe spring 43, thepiston 42 .is moved to 'the left, lowering the valve' member '33 .onto the seat 3 I, Iand terminatzlngthe iiow :of iiuid through the valve IDa. .Due to the inertia of the piston 42, it will tend to move somewhat beyond vthe position of balance between the vforcesexerted. bythe spring 43 and the pressure in the chamber 32. Such :additional movement is permitted by virtue of the sliding action of the valvestem 34 within the piston 42. Actually, due vtothe sluggishness of the piston l2, the valve member 33 will'be closed ata point atiwhich thezpressure in the working chamberA 32 :is .very slightly. greater than -the corresponding force .of the spring `113 at exactly the point of talosurapf` the valve member 33. rI'hus,;the piston 42will assume aposition of rest at which the face of the piston is slightly spaced from the flange, as illustrated in Figure 3. The result of thisfis that when the working pressure in the chamber `32 again drops below normal thepiston starts to'move to the right. and is already inmotion before it engages the'ilange 4 l I Thus, .the static friction of 1 the piston 42 againstrthe innerwall of thev housing25, is overcome before Vthe load of cracking the valve .3i-#33de added totheforces'resisting themovementof the piston. Also, the inertia of the piston 42 andthe valve stem.. 34 moving to the right give :an added initial impetus nto lthe Aripening force applied to the member 33.

The vforegoing di'scussionfapplies `only to the pressure reducing functionxof the vali/ew. rFor afmorefdetailed description of the presently preferred embodiment ofy the valve, reference should new be had to Figure. The. presently preferred valve I .is housed infa generally vrectangular body 50 having three'parallel longitudinal bores therein, and havingzinlet and .outlet passages l and 52, "respectively, which are threaded :toireceive the conduits i3 and l2, respectively, :as shown in Figure 4.

' A .Ofthe three longitudinal'bores, they uppermost contains a 'reverse flow check valve'assembly, in- 'dicatedgenerally by the :reference character 53; the central bore contains theA pressure reducing elements, indicated generally yby the reference character 54;"and the lowermost'borefcontainsa relief valve assembly, indicated generallyv by the l'characteri The three valve assemblies 53, 54 `and 55 'are Yinstalled into the valve 50 by insertion from the right-handfend of the body, `as viewed in Figure 5, and are secured therein by transverse pins 56 Vpressed into the'body.

. ReferringT iirst to the pressure reducing valve assembly 54 contained in the centralv bore, it will .be seen that the elements are essentiallyeduivaylent vto those described in connection with the simplified valve Illa. Fluid introduced thro-ugh the passageway l5| passes through a porous filter sleeveV 5l into a high pressurev chamber 58. From thehigh pressure chamber 58 fluid may,under certainv conditions, pass through a valve port 59 .into a'working'pressure chamber 69, A valve member A6| moved` by aV shouldered valve stem 62 controls the passage of .fluid through thev port 53.

The valve 'member 6| hasarelativelyloose nt with the valve vstem 62 whereby the .member .6i may rock slightly toseat itself vperectlyeon the valve port or 'seat 59. An internal sealing` gasket 53 is provided within the valve member 61 to prevent the escape of duid around` the valve stem '62. The valve member 6i, as in the previousfembodiment, is urged to the left by a compression spring 64.

Surrounding the valve stem 62 .at the'righthand end thereof is a sleeve'65, having .st-diameter slightly less than the opening of the l-valve port 59, the sleeve 65 being secured to the valve stem 52 -by a transverse pin 66. An internalsealing ring El prevents iiuid from escaping around the stemt-2 through the sleeve .65. The entire valve assembly, including the valve port or seat 59, the movable member 6I, the stem 62 the .porous filter sleeve 51., the compression spring .64, and the sleeve B5, is held into thecentral bore by means of a retaining bushing 68., and acover plate 69, held in place by the .aforementioned transverse pins 56,

The valve stem 62 is formed with three longitudinal flats 'lll whereby when the valve stemfis moved to the right to open themovable member Si, fluid may pass through the opening of the port 59 into the working pressurechamber. 60. .As in the previous embodiment, motion ofthevalve stem 62 to open the valve memberl is effected by a piston 'H urged to the right by a calibrated compression spring l2, and to the leftby iluid pressure in the chamber '50. The piston 'Hin its motion to the right, asjust described, engages a ange 'I3 on the valve stem 62 whereby to move the latter member to the right to open thevalve port 59 when the pressure in the workingpressure chamber falls below a predetermined value. As previously, .a portion 'i4 of the valve stem 62 projects through the piston ll, having sliding engagement therein, andy being sealed-by a sealing ring 1.5. The piston ll is installed from the left into the central bore ofthe valvebody 50 and is retained therein byfa locking ring 16 secured by a screw 1l.

The compression spring is also installed from the left and is anchored in the body 5..ag.ainst the piston 'll by an. adjustable threaded plug-17 which may be screwed into the .body 5U tov adjust the initial pressure yof the spring l2 against the piston 1I and thereby adjust-,to a predetermined working pressure in the chamber 60. The plug!" is locked inplace by a lock .nut-18, and is provided with a pair of Spanner wrench holes 19 which also serve as, breather openings.

.The operation of the reducer valve assembly 54 is'essentiallythe same as that described inconnection with the previous embodiment, When the pressure in the working pressure chamber falls below the predetermined value, the pistoni] moves to the right, engagingthe flange .13 and moving the valve stem.l2 tothe right,.whereupon the shoulder on. the stemy 62 adjacent the porte59, engages the movable valve member 6 I. and opens the same to allow additional high pressure iluid to ilow into the chamber 60. The diameter ofthe stem portion 74 is `slightly larger than the,Y port opening 5S which, in turn, is slightly larger than the external diameter of the sleeve ,B5 whereby the static pressures tend to hold the valve'member 6I in closed position. l

In the uppermost bore is installed the reverse ilow check valve assembly 53, which comprises a valve seat 80, a movable valve member 8l, normally engaged therewith,l` .a valve-closing ,spring 82` urging the valve member 8| vagainst the seat 80, all these parts being retained by a retaining bushing 83 secured in place by the aforesaid transverse pins 56. As can be seen in Figure 6, the retaining bushing 83 is cut away to form four longitudinal `splines 84 whereby fluid may escape around the valve member 8| when the same is lifted from the valve seat 8U. Fluid escaping around the movable valve member 8| may return to the inlet passage 5|, as can .be seen in Figure 5.

A diagonally drilled passageway 85 connects the central bore with the uppermost bore whereby the fluid chamber 60 is in communication with an upper valve chamber 86 adjacent the valve seat 80.

The purpose of the reverse flow check valve 53 is to return fluid from the portion of the working system connected to the valve I at the passageway 52 in the event of a drop in the supply pressure in the inlet passage which is normally higher than that in the working pressure chamber 60. The rat-e of the spring 82 is so calculated that upon the occurrence of a predetermined pressure differential between the pressure in the Working chamber and the pressure in the inlet passageway 5|, the valve 8| opens, permitting fluid to ilow from the chamber 6|) through the chamber 86, and the valve assembly 53, back into the normally high pressure system.

In the event that the pressure in the working chamber 60 should rise above a normal predetermined value but still be less than enough to open the valve 8|, it is desirable that such excess pressure be relieved. For this purpose, the relief valve assembly is provided in the lowermost .bore of the body 50. The relief valve assembly includeselements essentially equivalent to those in the reverse valve 53, the relief valve elements being a seat 90, a movable valve member 9|, a compression spring 92, and a retaining bushing 93, held in place by transverse pins 55. As can be seen in Figure 4, a pair of longitudinal grooves Se are formed in the bushing 93 whereby to permit the escape of fluid when the valve member 9| is lifted from the valve seat 90 by an excess of pressure in the exit passageway 52.

Forpurposes of describing the operation of the valve l0, let it be assumed that the storage pressure in the reservoir is on the order of 1500 pounds. Let it be assumed further that the desired working pressure in the cylinder I8 is 665 pounds.

The pressure of the spring l2 against the piston '1| is then adjusted by means of the threaded plug Tl until it is such that, with a pressure of 665 pounds in the chamber 60, the stem 62 has been moved to a point just in engagement with the movable valve member 6|. Thus, the pressure reducing valve assembly 5d will operate to keep the pressure in the chamber at 665 pounds so long as the storage pressure at the inlet passageway 5| is equal to or exceeds 665 pounds.

Let it be assumed further that it is desired to return iluid from the conduit IZ through the valve l0 whenever the pressure in the conduit i3 drops below 615 pounds. The reverse flow check valve assembly is then adjusted by proper selecltion of the spring 82 until a pressure diiferential of 50 pounds (665 minus 615) is required to open the valve member 8|. Under such conditions, a drop in pressure in the high pressure line I3 will result in a reverse flow through the valve assembly 53 to supply emergency pressure to such portions of the working system as may be connected to the conduit I5. 1

, Finally, if the pressure in the chamber 60 rises above 665 pounds, it normally cannot escape through either the reverse flow valve assembly 53 or the pressure reducer valve 54 since the pressure in the high pressure chamber 58 is in the neighborhood of 1500 pounds. Such excess pressure in the chamber 60 can escape, however, through the relief valve assembly 55 inasmuch as the compression spring 92 is so selected as to permit opening of the valve member 9| when the pressure thereagainst exceeds 665 pounds.

Thus, it will be seen that through the incorporation of a valve embodying the present invention, a variable high pressure storage system is possible, wherein the working pressure is accurately maintained at a constant value, and wherein emergency pressure may be made available in the event of a failure of the storage reservoir.

While the valves shown and described herein are fully capable of achieving the objects and providing the advantages hereinbefore stated, it will be realized that they are capable of considerable modification without departing from the spirit of the invention. For this reason. I do not mean to be limited to the forms shown and described, but rather to the scope of the appended claims.

I claim:

1. For use in a iiuid pressure servo system of the type having a high pressure supply system including a storage reservoir and a pressure actuated motor system adapted to operate at a work'- ing pressure less than that of said reservoir, a. iuid pressure regulator comprising: body means having a rst fluid connection for communication with said reservoir and a second uid connection for communication with said motor system; means forming rst and second passages having fluid connection adapted to be connected'between said reservoir connection and said motor system connection; a member in said rst passage adapted to control ow of fluid therethrough; pressure sensitive means responsive to said working pressure at said motor system connection and connected to move said member and arranged to positively open said first passage when said Working pressure falls below a predetermined value; check valve means in said second passage adapted to prevent fluid flow therethrough from said reservoir connection to said motor system connection; yielding means adapted and positioned to urge said check means to closed position, said yielding means being further adapted to yield to opening movement of said check valve means upon a predetermined excess of pressure at said motor system connection over that at said supply reservoir connection; and pressure relief means in said regulator communicated with the fluid connection for said motor system adapted to release uid from said motor system when the pressure thereof exceeds said working pressure.

2. A pressure regulator comprising: a body having formed therein normally high and low pressure fluid connections and at least two passages interconnecting said connections; a valve member in a first of Said passages responsive to pressure at said high pressure connection to normally close said rst passage; pressure sensitive means in said body responsive to uid pressure at said low pressure connection and adapted to move said member to open said first passage when said fluid pressure at said second connection falls below a predetermined working value: and check valve means in said second passage independent of,v said valve member-:and adapted toe normally close said 4 second 'passage whenever thev press'uieat said high pressure-connection exceeds-that at said lowpressure: connection', said check valve' means including yielding means adaptedfand po'sitionedto urge said check mean-s tot ciosed position; said` yielding means being 'further adapted to yield toV opening movementvof said check means upon a predetermined excess of; pressure at Isaidse'cond connection over that ait-said `,iirst fconnection.i

3. The'constructionset forthfinclair-n' 2 further characterized .by Ihaving vflu-id Yrelease means insaid; body communicated with said second connection and adapted to release iiuid from said bodywhen'ever the uid pressure at said second connection exceeds by-agiven amount said predetermined working. value2 4.- yIn a duid-control valve, the combination of: a body having lformed therein,v Iinlet and outlet fluid connectionsv and a passage therebetween; an annular fluidA portin said passage Ipositioned todivide the samevfin-tok two intercommunicated chambers upstream-and downstream from said port; amovableannular valve member in said upstream chamber adapted to contact .said varmular valve Aport to close saidpassage; a first compression spring in said upstream chamber positioned and adapted to urgejsaid valve'member ina closing direction; a circular opening in said upstream chamber coaxial with said port and having aldiameter slightly less than that of said port;. lmeans `forming a `relatively large cylindrical opening in saiddownstream chamber; apiston sealably and slidably positioned in said cylindrical opening for movement toward and away from said port; a second compression spring engaged with said piston and adapted to urge the same toward said port; anadjustableabutment for said second spring positioned and adapted to adjust the j :ir'essurev of said spring'y against said piston; a circular opening. in said piston-coaxial with said portrandV havngpa. diameterl slightly larger than that of said port; a valve stem having cylindrical end portions sealablyand slidablypositioned in-said upstream chamber openingiand said piston opening with its'ends exposed to external pressure adjacent said openings,said valve stem yhaving lan abutment formed thereon adjacent said piston whereby inward motionpof saidVA piston .engages said abutment and moves said, stemf inwardly toward-:said port, and said stem having shoulder meansiormed therein adjacent; said; port, said shoulderv means 1 being adapted to engage said valve member upon-movement of said stem in said inward direction to open said valve member whereby decrease of pressure in said'downstream Achamber to a predetermined value permits said second compression spring. to move said piston inwardly to engage: said ,abutment 'and move' .said stem ,to open said'valve nieiribi and increase in said downstream chamber pressure moves said piston outwardly in opposition to said compression spring to permit said rst compression spring to close said valve member and whereby said piston may move outwardly after closure oi said valve member.

5. The construction set forth in claim 4 further characterized by having formed in said body, a second passage communicating said upstream and downstream chambers, said second passage having a check valve means therein, positioned and adapted to normally prevent flow from said upstream chamber to said downstream chamber yand said checkrvalvemeans includingA a spring urging `the sameyinto closed position; said spring beingadapted `tonyield upon a pref determined excess of pressure in said downstream chamber over that of said upstreamchamberl whereby to opensaid check valveand permit counteriiow of fluid through said second passage upon failure of fluid pressure invsaidupstream chamber.

6.1The4 construction set forth ,in claim 5v fur:- ther characterized by having a springclosed pressurev relief val-verv in said Vdownstream y cham-f ber adapted togopen and release fluid from said downstream: chamber upon the pressure therein exceeding a predetermined.' value.`

7.*Invafluid control valve, the combination of: .a .body having a uidpassage therethrough; an intermediate valve port of predetermined area; formed in said Vpassage andA dividing thesame into upstream. and' downstream chambers; an opening in the wall of eachof said chambers', axially aligned withV saidport, the open-inginsaid upstream chamber being slightly smallerthan the area of said port, and thearea of the opening said downstream chamber, being. slightlylarger than ,said port; a valve stem' seal-A ablyandslidably carried in said openingsgand extend-ing .through said port; said; stem vhaving a portion reduced in cross-section intermediate its ends tov leave an annularA opening throughsaid port around said stem; an annular valvememberv sealably and slidably carried by said stem and said reduced portion and positionedtoclose said port opening; yielding means in-said up.- stream chamber engaged with said annular valve member to urge Athe same in a closing vdirection abntments on saidl stem upstream anddown-f. stream from said valve member to limit the movement thereon of said stem whereby axial; movement of saidstem inan upstream directionI lifts said valve vmember to open saidport, and axial movement of said stem ina-downstream direction urges said valvemember against said; port; and whereby fluid pressure ineitherot said chambers urgesrsaid valve;memberin.- af closing direction a movable lportioninthe wall of :said downstream chamber externally exposed: to: atmospheric-pressure and positioned adjacent said gstem; anda ilost :motion connection between. said w'all portion ,and stem to move th'eflatter to liftzsaid valvemember upon pressure reduc-r tion responsivemovement ofvsaid wall portion:

8; In-,a fluid. control valve,l thercombination of: abody rhaving a iiuid passage therethrough; an intermediate valveport of-predetermined area-` formedfinv said passage vand dividing thesame into upstream and downstream chambers; anopening in the wall of each ,of said `chambers,v axially'raligned withsaidlport, the opening in said-` upstream chamber being slightly f smaller than the area of said port, and the areazotthe opening in said downstream chamber being slightly larger than said port; a valve stem sealably and slidably carried in said openings and extending through said port, said stem having a portion reduced in cross-section intermediate its ends to leave an annular opening through said port around said stem; an annular valve member sealably and slidably carried by said stem on said reduced portion and positioned to close said port opening; abutments on said stem upstream and downstream from said valve member to limit the movement thereof on said stem whereby axial movement of said stem in an upstream direction lifts said valve member to open said port, and axial movement of said stem in a downstream direction urges said valve member against said port, and whereby fluid pressure in either of said chambers urges said valve member in a closing direction; a valve spring in said upstream chamber engaged with said valve member to urge the same in a closing direction a movable portion in the wall of said downstream chamber externally exposed .to atmospheric pressure and positioned adjacent said stem; and a lost motion connection between said wall portion and stem to move the latter to lift said valve member upon pressure reduction responsive movement of said wall portion.

9. In a fluid control valve, the combination of: a. body having a uid passage therethrough; an intermediate valve port of predetermined area formed in said passage and dividing the same into upstream and downstream chambers; an opening in the wall of each of said chambers extending to the exterior of said body, said openings and port being axially aligned; the opening in said upstream chamber being slightly smaller than the area of said port, and the area of the opening in said downstream chamber being slightly larger than the area of said port actuating means including a movable portion in the wall of said downstream chamber externally exposed to atmospheric pressure and adjoining said opening therein and a valve stem extending through said openings and port and sealably and slidably carried in said openings, said stem having an abutment thereon engageable by said wall portion and a portion reduced in cross-section at said port to leave an annular opening therethrough around said stem; an annular valve member slidably and sealably carried on said reduced portion positioned to close said port opening; and a second abutment on said stem positioned to engage said valve member and lift the same upon axial movement of said stem toward said upstream chamber; and yielding means in said upstream chamber engaged with said annular valve member to urge the same in a closing direction.

10. The construction set forth in claim 9 further characterized by having formed in said body, a second passage communicating said upstream and downstream chambers, said second passage having a check valve means therein, positioned and adapted to normally prevent ow from said upstream chamber to said downstream chamber and said check valve means including a spring urging the same into closed position, said spring being adapted to yield upon a predetermined excess of pressure in said downstream chamber over that of said upstream chamber whereby to open said check valve and permit counterow of fluid through said second passage upon failure of uid pressure in said upstream chamber.

11. In a uid control valve', the combination of: a body having formed therein an inlet, an outlet, and a passage therebetween; a fluid port of predetermined area in said passage to divide the same into two intercommunicated chambers upstream and downstream from said port, said upstream chamber having an opening of predetermined area formed therein in addition to said inlet; a movable valve member in said upstream chamber having a central bore and a surrounding portion adapted to cooperate with said port to close said passage; a movable portion in the wall of said downstream chamber externally exposed to atmospheric pressure and having an opening of predetermined area formed therein in axial alignment with said port and said upstream chamber opening; a valve operating member sealably and axially slidably positioned in said openings and extending through said bore, said member having a rst abutment adapted to engage said valve member whereby the latter, when closed, is acted on by force equal to a-b-l-c-d, where a is equal to said port area times the pressure in said upstream chamber, b is equal to the area of said upstream chamber opening times said upstream chamber pressure, c is equal to the area of said opening in said wall portion times the downstream chamber pressure, and d is equal to said port area times said downstream chamber pressure; and abutment means on said operating member engageable by said wall portion upon pressure responsive movement thereof whereby to open said valve member upon occurrence of a predetermined pressure in said downstream chamber.

LEE E. BALDWIN.

References Cited in the le of this patent UNITED STATES PATENTS Number Name Date 913,853 Rowntree Mar. 2, 1909 1,131,341 Dieter Mar. 9, 1915 1,650,150 Nelson Nov. 22, 1927 1,731,145 MacMillion Oct. 8, 1929 1,836,740 Albers Dec. 15, 1931 2,005,445 Wiedhoit June 18, 1935 2,189,221 Paine Feb. 5, 1940 2,232,038 Stone Feb. 18, 1941 2,272,243 Jacobson Feb. 10, 1942 2,314,672 Veenschoten Mar. 23, 1943 2,316,445 Marshall Apr. 13, 1943 2,365,650 Shaw Dec. 19, 1944 2,442,635 Bennett June 1, 1948 2,524,264 Knox Oct. 3, 1950 FOREIGN PATENTS Number Country Date 178,207 France Aug. 27, 1886 785,116 France May 13, 1935 

